Control system



0a. 13, 1931. BRISTOL 1,821,351-

CONTROL SYSTEM Filed March 9. L929 "4 Shets-Sheet 1 nZOr Oct. 13, 1931. E. s. BRISTOL 1,827,351

v CONTROL SYSTEM I Filed March 9. 1929 4 sheet s-s hee t 2 Oct. 13, 1931. 4 E. s. BllsToL I 1 1,827,351

CONTROL SYSTEM Filed March 9. H29 4 Sheets-Sheet 5 7 Oct. 13; 1931. E, BRISTOL 1,827,351

CONTROL SYSTEM Filed March 9. 1929 4 Sheets-Sheet 4 T 34L 4 j? I i l i f superimposing upon the Q 'afiecting pressure,

Passe: Uct. 13.1931

1umrso STATES raraurorrics EDWARD s. BRISTOL, or PHILADELPHIA, rENNsYLvA'Nm, AssIGiI'on. 'ro LEEDS a NORTHRUP ermany, or rnmenmrnm. PENNSYLVANIA, A coBPoRArIoN' or PENNSYLVANIA.

- CONTROL mam I Application am March 'a, 1929. serial r. 345,353.

My invention relates to a system of control or regulation of the magnitude of a quantity or condition; and moreparticularly relates to a system of regulation of the pressure of a fluid, and moreparticularly the regulation of the pressure of steam in a steam generating system. v r

In accordance with my invention, the application of two or more agents, or of the com- 1 o ponents of an agent, upon which the magnitude of a quantity or condition depends, is normally controlled in response to changes of the magnitude, and .thenormal control is modified directly in response tobhange in the magnitude and independently of the efiect of the normal control. I

In accordance with my invention, there is provided mechanism for automatically controlling two. or more pressure-changing 2 agentsor factors of the same or diife-rent character in response to changes inrate of flow of a. fluid, or an efiect representative thereofi for example, a pressure change, in combination with means-for automatically automatic regulating mechanism a control independent of said agents. or factors, or res onsive directly to movement of a member 0 the-control mechanism movable in response to pressure change, 3 for the purpose of eflecting change oi the fluid pressure in opposite sense, to a predetermined standard, if desired, and at a suitable rate. 1

.' More particularly in accordance "with my invention, there is provided mechanism for controlling automatically pressure-changing agents or components of an agent oragents, in-response tdpre'ssure of, or rate of flow of,

v a fluid, in combination with means for super- 0 imposing automatically uplonth'e aforesaid automatic regulating mec anism a control independent-of said agents orvcomponents movement of'amember of the control mechanism movable in response to-change in pres sure, or rate of flowfof the fluid, for the purose of eflfecting change of the fluid ressure 'o osite sense, to a predetermine stand ard i desired, and atsuitable rate.

More particularly in accordance my ed by mechanism of the character aforesaid or responsive directly to invention, the ressure control is that of steam delivered y one or more steam generators, and the control of the pressure is efiectoperating to control in any suitable way the rate of combustionin the generator furnace or furnaces. 4 p

' My invention resides in asystem and apparatus of the character hereinafter do I scribed and claimed.

For an illustration of some of the various forms my invention may take, reference is to be. had to the accompanying drawings, in which; f

Fig. is an illustration of an embodiment c5 of my invention, partly diagrammatic, and

partly in section and elevation.

Fig. 2 is an illustration of another embodiment of my invention, also partly diagram- I matic, and partly in section and'elevation. '10

Fig. 3 is a fragmentary side elevation of part of the structure of Fig. 2.

Fig. 4 is a side-elevation, partly in vertical section, ofa further form of apparatus utilizing my invention.

Fig. 5 is an elevational view, partly in sec-' tion, of a control balance utilized in the sys-' tem of Fig. 4.-

Fig. 6 is a view, partly in elevation and partly diagrammatic, of the control circu t so of the system of Fig. 5. 9

Referring to Fig. 1, B is a steam boiler or generator comprising a-drum D in communication with the water tubes T, which latter are disposed in a heating chamber comprising the furnace or fire chamber F from which the hot gases pass around the tubes T and thence outwardl through the stack S- providedwith the amper d operable by hand or automatically through the pivoted steam-consuming devices. Steam is supplied Q5 through-the pipe e to the engine or motor f, which drives the'stoker g which, delivers fuel to the fuel bed ia/dis osed upon the grate i, i upwardly through which and the be hair is supplied atjvarying rate by theiair blower 1 A driven by any suitable means, as, for example, the electric motor M, which is in turn controlled in response to variations in the pressure of the steam delivered by the generator B.

Connected with the conduit C is the pipe 5, through which the steam pressure is aplied to the interior of the chamber is closed y the flexible or yielding dia hragm m, upon which is carried the knife e ge or pivot n, upon which rests the lever or beam aprovided with the pivot or knife edge 12 engagin the under side ofthe abutment g. Movab e along the lever 0 is the member 1*, which may be secured thereto in any of its adjusted positions by the set screw 8. Pivoted to the fixed member t at u is the. lever 0, along which is movable the member w, which may be secured in any of its adjusted positions. by the set screw as; The link 3 is plvoted at its opposite ends to the members '1' and 'w,

whereby movements or deflections of the lever 0 are imparted to the lever v. B ad- 'justing the members 1* and w to diflerent positions along their respective levers 0 and 2:,the ratio of angular movements of the levers 0 and 'v is variable or adjustable for the purpose of varying with respect to the pressure change effective upon the diaphragm m the magnitude .ofthe resultant control effect, as, for example, control of the speed of the motor M and therefore control of the rate of combustion in the generd h lidt 1th osin t e' ressure app e o e unddi side of the liever 0 by the diaphragm m is the weight a, hung by the knife edge a1 upon the lever 0.; For operating cumulatively with the weight 2 upon the lever 0 there may be utilized the "spring b1, connected at its one end to the lever 0 and at its opposite end to the member 23, the tension of the spring bein adjustable by the screw 01. The effect of t e spring 61, if and when employed, isrto reduce the extent of motion or deflection of the lever 0 for a given change 'h1' to atmosphere. In the chambers p1 and dlis contained liquid '51, which may be of any suitable character, as water, oil, etc. The spaces in the chambers all and g1 above the liquid therein are connected through the flexible tube jl.

Carried by and insulated from the lever '12 is the movable contact [c1 of a rheostat comprising the resistance ml, the amount of which in. circuit is increased by downward field of the motor M is weakened or strengthened as the contact 701 descends or ascends,

effecting corresponding increase or decrease of speed of the motor M, and therefore of the blower A, andthereby increasing or decreas-' ing the rate of combustion of fuel in the gen-.

erator B.

While the weight .2, spring b1 and chamber all are shown as applied directly to the lever 0, it will be understood that any one or more of them may be applied to the lever 'v to apply thereto a downward force to the left of its pivot u. And it will be understood that these members, or equivalents of them, may be similarly applied to the secondary levers corresponding with lever 'v of any of the other arrangements hereinafter described.

The operation of a system of the character illustrated in Fig.1 as thus far described, is as follows: I 1

Assuming that the standard or reference pressure of-the steam delivered through the conduit 0 shall be, for example, 250 pounds per square inch, the normal control, that is,

the control effected by the lever 0 under the control of the diaphragm m and either or both the weight a and sprin 61, but without the chamber 011, or without dhange in amount of liquid therein, will, for changes of load within suitable limits, maintain the header pressure withinthe range of, for example, 245 to 255 pounds per square inch.

Upon occurrences of load or increase of load upon the generator B, the pressurewill f tact Isl descends, cutting resistance intothe I field of the motor m, an thereby correspondingly increasin the speed of the blower A and the rate'b combustion. The speed of the blower A effected by the aforesaid descent of contact 701 may be such as to increase the rate of combustion to such magnitude that during the persistence of the same load which caused the descent of the diaphragm m the steam pressure of the generator will be main- .tained at the aforesaid magnitude of 247 pounds. Such normal control may effect, as

stated, the maintenance of the steam pressure during .persistenceof load at the sub normal pressure of, say, 2427. pounds, or the ad ustments or proportions may be such that the rate of combustion will permit the steam thereon a compounding control, efl'ective im- I mediately the lever 0 deflects. The super-' posed or auxiliary control is direct, in the sense'that it is dependent directly u on the deflection of the lever 0, and not'in irectly upon any force due to or representative of a change effected through the normal control aratus. More specifically in the example illustrated, the superposed or the compound control is effected by 'flow'of liquid through the throttle valve ;1 and tube- 61 into the chamber d1, thereby applying greater weight to the lever 0. fore directly applied, and directly and'immediately in response to deflection of the lever o, and in thi'scinstance greater asthedeflection of lever 0 is greater; it is not due, indirectly to the efi'ect of the control, as pf the blowerA or any other steam-pressure-changing means, as effected in response to deflection of the lever 0. When. the lever arm 0 finally'attains equilibrium after a change of load, the superposed control has acted to change the loading weight on lever 0 ina predetermined manner, so that the steam pressure attains a predetermined value for. each position ofthe regulating mechanism.

Because of the increased weight applied to the lever o by the liquid passing from chamber 91 into the chamber (11, the control is cient to maintain the steam compounded in the sense that notwithstanding the persistence of the load upon the generatonB which caused the fall in steam pressure, the-speed of the blower will be such as to effect a rate of combustion more than suflipressure at 247 pounds, and will cause it to rise or return to 250 pounds; or the control may be overcompounded and cause a rise in the steam pressure during the persistence of the load to a value even higher-than 250 pounds. The

, nature of the compounding action is predetermined as desired by suitably fixin the size and shape of the chambersdl an g1.

The effect of the superposed or compound I ing control is, therefore, to cause an amphfica- BxOItlOILOP exaggeration of the normal control an agent aflfecting the rate 0 in the example illustrated, or any other con- 3 to effect the application of an agent, such as combustion dition or factor upon whose magnitude depends the ma nit-u e ofthe steam pressure. The thrott e valve ;1 1s provided topm- This bias or force is therelong or retard the flow of liquid from cham- I ber g1 into chamber d1 upon downward deflection of the lever 0 or to delay or retard the flow in reverse direction from chamber 7 d1 into chamber 91 upen upward deflection of v lever o. By preference, the valve fl is so nearly closed as to introduce a considerable time factor as regards the application of the superposed or auxiliary control to prolong the desired steam pressure change throughout a period of, for example, ten. to fifteen minutes, more or lesse It will be understood that any number of steam generators may be simultaneously controlled by one and the same-mechanism in res onse to their common steam pressure. In suc case, the blower A may supply air for all of the generators of the battery or each generaor may have its own blower driven by an indlvldual motor. For example, in the two generator installation of Fig. 1, the speed of the blower A1 driven by motor M1 is determined by the position of the contact k2 alongresistance m2 connected in circuit with the field winding of motor Ml by conductors 92, p2. To eii'ect simultaneous movement of contact arm 7:1 controlling the speed of blower A and of contact arm E2, the arm'o' plvotally supported upon standard It is connected to arm 'v, for example,-by a link Z, the ends of which are pivotedto slidable member w and w, respectively, the latter being adjustably-secured to arm '0 by a set screw The change in the rate of combustion of boiler B1 for a given change in pressure of steam in the common header C of boilers B Y and B1, due to change in load, for example,

and the relation between the rates of com bustion of the boilers is determined by positions of members 1,40, and w along leverso, 'v, and Q) respectively. Alternatively, the resistances m1 and m2 may be designed toeffeet desired changed in resistance for movement'from one position to another of the cooperating contact arm, equal extents of move.-

menteffecting, if desired, different resistance changes in difi'erent regions of movement.

While for purposes of illustration, I have described the control of the rate of application of air to a combustion chamber of a steam generator, it will readily be understood by those skilled in the art that the control ef-l fected by deflection of lever 0 may be of any 1 other combustion factor, as rate of delivery of fuel, position of damper d, or any two org more of them, or of any other agency, in syssteam, whose magnitude,"rate of application of agent, or position may determine 'or affect the pressureto be regulated. In the arrangeindicated in-Fig. 1, or in asystem of any other character above referred to for 'con-130 tems other than those for the generation of I ment ofFig. 2, the control mechanismtherer Qf' disclosed nay be used in a system such as trolling the magnitude, rate of application, or position of a control agent.

Referring to Figs. 2 and 3, there is illustrated an arrangement in which along the secondary lever 112 is adjus able the member 11, to which there is pivoted the link 81 piv ,oted at its upper end to the member 61 ad-' justable alon the member ul carried upon the piston ro '03, upon which is secured the piston wl movable in the cylinder :12. To the rod '03 is connected also the chain c, utilizable for varying the position of the damper d to thereby vary the rate of combustion of the generator B, as when natural draft is used, or as when forced draft is supplied so as to maintain a desired pressure beneath the fuel bed h, as will be understood by one familiar with the art. The lower and upper ends of the cylinder'wfl are connected through the passages yl and 21, respectively, with the upper and lower ports a2 and b2 of the pilot valve structure comprising the chamber 02, in which is movable with respect to the ports a2 and b2 the slide valve 012 operated by the rod 62 pivoted to the lever '02 at f2. Fluid under pressure, as steam, air, water, etc., is delivered through the. pipeg2, and directed according to the position of the valve (12 into the cylinder 002 on one side or the other of piston 102, the fluid being exhausted through the exhaust or discharge outlet 122.

By the adjustment of the members 11 and t1 along the lever '02 and member ul, respectively, the distance between the pivot f2 and the pivotal mounting of the lever upon the membert1 through the .ink 81 is varied to procure any suitable ratio of movement of the slide valve d2, whose movement is further \r afl'ected by the ratio of movements, of the levers 0 and v2as determined by the positions of the members 1' and 'w upon the levers '0 and '02, respectively.

In general, the operation is similar to that described in connection with Fig. 1, in that the flow of liquid from chamber g1 into chamber dlupon downward deflection of the lever 0 effects a superposed or amplified control causing the piston 102 to move in such a direction and t9 such extent as to move the damper d in such direction and to such extent as to effect a rate of combustion which may be such either as to maintain the pressure corresponding with the increased load, or as to cause such pressure to rise and return to or beyond the standard or reference pressure.

The damper d in the stack. S1 of steam generator or boiler B1 may be 'operated simultaneously withdamper d and moved toequal or different extent as desired. Obviously any number of dampers may be simultaneously controlled by movement of plunger 102. The relative positions of dampers d, (2, etc. for any load upon the group of boilers may be determined, for example,

bychanging the length of respective chains 0.

As before stated, movement of arm 0 may additionally be utilized to change the position of one or more rheostat contacts controlling the speed of blower A and/or. blower A1.

The piston 102 by its motion reacts through the lever '02 upon the valve d2 to return it to or toward its port-closing position. In the example illustrated, a downward deflection of the lever 0 causes upward movement of the piston Q02 and of chain c, and reacts u on the valve. d2 to return it upwardly towar or to port-closing position.

WVith structure of this type there is a definite position of the piston'w2 corresponding to any position of the arm 0 within the workin range. The use of the piston 'w2 and'its ad uncts of the character described may, as indicated, be utilized in lieu of or in addition to the motor M and its control of Fig. 1:

Referring to Fig. 5, a receptacle 1 with the member 2 forms a sealed or pressure-tight chamber within which is disposed the arm or beam 3 having. the upstanding arm 4 secured upon a shaft 5 carrying at its opposite ends knife edges resting upon fixed abutments, whereby the members 3 and 4 are delicately and nicely pivoted for movement about an axis which, in the example illustrated, is horizontal.

Disposed in the vessel 1 is a body of any suitable liquid, as oil, rising to a suitable level, for example, that indicated at 6.

Attached to the beam 3 is a bell or openended chamber 7, whose mouth or open end is disposed below the level 6 of the liquid. Secured to the beam 3 is the member 8, projecting into the liquid, and compensating for changes in height of liquid level 6. Adjustment of normal position of beam 3 may be efiected by a weight (not shown) adjustable longitudinally of the beam.

Through a pipe 9 flows a fluid, such as air,

gas. etc., in response to changes in whose rate I 12 to the interior of the chamber above the liquid level 6; and from the other side of the orifice l1 connection is made hrough the pipe 13 and the'pipe 14 tothe interior of the bell 7 above the liquid level 6, the pipe 14 preferably being separate -from the pipe 13 and threaded to the receptacle 1, as indicated in Fig. 5.

The difference between the pressures inside and outside of the bell 7, as effected by the connections 12 and 13, may be adjusted or varied, for a given rate offlow of fluid through the pipe 9, by recourse to the bleeder pipe 15 connecting the pipes 12 and 13 and 0011- trolled by any suitable throttling means,- as T a needle valve 16.

Secured upon the upper end of the arm 4 is a magnet coil B2, disposed between the stationary coils C2 and D2 carried upon the stationary supports 17, suitably carried and supported within the chamber.

Common to two or more of the coils is the iron or other core A2, having attached to one end thereof a cord 18, or equivalent, passing through the eye 19in a bracket 20, and having attached toits other end the weight 21'. a

Attached to the other end of the core A2 is a cord 22, or equivalent, passing through an eye 19 in a second bracket 20. The cord 22 is wrapped around and has its end secured to fllG'SPOOl or drum 23 secured upon the rotatable shaft 24, extending through the pressure tight stufing box or gland 25 to them;- terior of the chamber, where there is secured thereon the disc or wheel26, which may be suitably marked or indexed with graduations,

- with which co-a'cts the combined index or pointer and disc-clamping member 27 carried by the bracket 28 secured to the chamber.

As diagrammatically indicated in Fig. 6,

A there is carried by the movable arm 4 a contact 292 co-acting with the laterally adjusta ble stationary contacts 302 and 312. The fixed and movable contacts are utilized for controlling any suitable electric circuit for effecting any desired orsuitable result, as a control.

As illustrated in Fig.- 6, stationary con tacts are connected by conductors 32 and 33,

respectively,- with the external terminals of two seriesfield windings of a reversible electric motor M3, the other terminals of the series field windings being connected to the same terminal of the armature of. the motor,

- whose other terminal connects byconductor 34 to one terminal of a source of current, whose other terminal connects by conductor 35 with the movable contact 292. The contacts 292, 302, 312 may controlrelays which in turn control the motor The translating device or motor M3 may be utilized to effect any suitable or desirable operation or control. In the example illustrated, the motor M3 rotates the stem 36 of a valve V which controls the rate of flow of fluid through the pipe 9.- As generically indicated by the pinion 37 and gear 38, there is provided between the armature shaftjof the motor M3 and the driven member, as valve stem 36, reduction gearing, whereby the motor armature may make several or many revolutions for one revolution of the stem 36,

for effecting niccty of control and for intro- 'ducing a time lag of suitable magnitude, if

desired.

When the rate of How of fluid through the pipe 9 is too great, the difference between the pressures within and without the bell 7 is of opening a magnitude sufficient to overcome the magnetic force exerted by the coil B2 upon t e stationary coil or coils C2, D2, all 0 are connected in series with eachother and traversed by a control current, with the result that the arm at is' tilted to close the circuit from the current source through one of the field windings and the-armature of the motor M3, causing rotation of the valve stem 36 in such direction as to reduce the rate of flow which, upon attaining the desired magnitude, causes such a force to be exerted upon the beam 3 that the contact 29z resumes its mid or neutral position indicated in Fig. 6,

the circuit of the motor M3. Similarly, when the rate of flow falls below the desired magnitude, the beam 3 is tilted in the opposite direction, closing the circuit through the other series field winding and armature of the motor M3, causing the armature to rotate in opposite direction fr'om that of the preceding case, and rotating the stem 36 to open the valve V, and the resultant increase of rate of flow causes the force exerted by the diiferential pressure upon the beam 3 to increase and overcome the force exerted by the control coils until the contact 292 again resumes its mid or neutral position when the circuit of the motor M3 is opened.

To vary or adiust the magnitude of the magnetic force as exerted between the fixed and movable coils, for agiven magnitude of the control current flowing therethrough, and thereby vary the relation between the mag nitude of control current and the diflerential pressure exerted upon the beam 3 for a given magnitude of flow of fluid through the pipe 9, the disc 26 is turnedin suitable direction to efl'ect movement of the core A2 to the right or the left, with-the result that for a given which magnitude of current through the fixed and movable coils the amount of force exerted between them is adjusted or varied to suitable magnitude. Accordingly, by varying the position of the-core A2 there is varied the effect of a control current of a predetermined magnitude upon the range or amount of control eflected by the circuit controlled by the fixed and movable contacts.

"Or without changing the position of the core A2,'a change in the opening of the needle valve 16 changes the force exerted upon the beam 3 in response to a predetermined rate of flow of fluid through the pipe 9.

It will be understood that either the core A2 alone may be shifted in position, or the valve 16 alone may be adjust'ed,-or both may be adjusted to afiect the relation between the rate of flow of fluid and the magnitude of the control current. Variation of position of the core A2 varies the constant of the instrument or the relation between the magnitude of the Variation of the position of the valve 16 for supporting combustion, the hot passing upwardly around the water tubes,

the control'balance.

By the utilization of a movable coil B2, with one or more fixed coils, C2, D2 the force exerted as between the movable c011 and the fixed coil or coils is proportional to the square of the magnitude of the current traversing the.coils, and the force exerted upon the balance arm or beam 3 is proportional to the square of the rate of flow of fluid through the pipe 9, and accordingly the rate of flow of fluid is proportional to the magnitude of the control current. Reference is had to Fig. 4, illustrating a group of controls for a boiler or steam generator for effecting maintenance of substantially predetermined standard steam pressure notwithstanding wide fluctuations in load upon a plant. i a The steam generator may be of any suit able type, and in the example illustrated, comprises water tubes, associated with suitable baffle walls 40 for directing the hot gases in a circuitous path, and communicating with the drum D, from which steam is discharged to header G. Fuel is delivered into the chute or hopper 43 on to the travelling grate or stoker structure g, air being delivered through the duct.45, as from a blower, under control of the damper 46, to the under side of the grate and through the fuel bed thereon gases downwardly between the walls 40 and upwardly to the breeching, stack or chimney S controlled by the damper d.

The pressure of the steam in header C is communicated through thepipe 9' to the chamber is, one of whose walls is a flexiblediaphragm m acting through the post 52 upon the lever 0 fulcrumed upon the knife ede and having the attached biasing weight 2.

Attached to the lever 0 at a desired point is an elastic member, preferably a helical spring 61.

A link member y transmits movement of lever o to contact arm '0 pivoted to fixed support t and coacting with resistance ml to vary, in response to changes of steam pressure operative upon the underside of diaent upon at least three different factors; i. e.,

boiler, pressure, pressure drop between the boiler" and point of attachment of pipe 7', and

velocity head of steam flowing through pipe 42, the last two factors being definite functions of rate of flow of steam through pipe 42. Since the velocity head is ordinarily a negligible factor'with the pipe. j connected to 42 adjacent 'a' boiler drum D, the pressure within chamber is closely approximates that of the boiler whereas, with pipe j connected to steam main or header C at a point between Y which and the boiler there exists considerable pipe line resistance, the pressure within chamber In is very largely, or to a considerable extent, aflected by changes in pressure drop through the discharge pipe 42. In the latter case with the pipe line resistance commonly encountered in boiler plant practice,

the pressure drop due to rate of flow is the controlling or dominant factor so that presr-urechanges in boiler plant header are close .ly related to variation in steam flow.

, At X, Y and Z are indicated control balances of any suitable character, and preferably of the character illustrated in Fig. 5. As indicated in Fig. 6, the c'ontrol circuit includes in series with each other the fixed and movablecontrol coils B3, C3, D3 of the auxiliar controller or control balance X, the fixe and movable control coils B4, C4, D4 of the auxiliary controller or control balance Y, the fixed and movable coils B2, C2, and

D2 of auxiliary controller Z,-and, when suitable ordesirable, the ammeter, recording'am- -meter or integrating'current meter I. The

by any suitable motor, as, for example, the

steam engine 6, suppliedwith steam from any suitable source, for example, the pipe 42 or header C, through the pipe e controlled by the valve 68, in turn controlled by a reversible electric motor M3, preferably through suitable reduction gearing, not

shown, which drives the oscillatory lever 69,

connected through suitableel'ements to the movable member of the valve 68. The mov able contact 29w of the control balance X is connected with the conductor 66, while the stationary contacts 30:): and 31m connect to J the, series field windings of the motor M3, whose armature connects with the conductor 65. A movable contact 70 and a fixed contact 71 constitute a limit switch in the field circuit controlled bycontact 30m; and similar contacts 7 2, 73 constitute a limit switch The lever 69 'carries the members 74, which are adapted to engage the movable contacts 70 and 7 3 at the limits of travel in opposit directions to break the motor circuit.

The engine 1) drives an air blower K which effects, through pipe 13c, corresponding with.

pipe 13 of Fig. 5, within the bell on the balance arm of the controller X a pressure dependent upon the speed of the stoker g, The

space above the liquid in the controller X communicates with the atmosphere through-- the pipe 126, whereby there is effected a differential pressure acting upon the tilting balance arm, the effective pressure justable, if suitable or desirable, necting the pipe 13c to atmosphere a needle valve, such, for example, Fig. 5.

The damper 46 in the air-supplying duct 45 is actuated by the reversible motor M4 as by conthrough as 16 of which, preferably through reduction gear-.

ing, not shown, moves the lever 69, operas tively connected to the damper 46, in opposite directions, the lever 69- controlling the limit switches, as described in connection with the motor M3. The movable contact 29 of the control balance Y, connects with the conductor 66, while the stationary contacts 303 and 31y connect with the series field windings of the motor M4.

The tube 12/ extends into the air duct 45 and connects with the chamber of the control balance Y, and the pipe 13/ communicates with the interior of the bell ofthe balance Y and terminates within the duct 45 at an extension facing the direction of the air current, whereby the differential pressure representing the rate of flow of air is exerted upon the balance arm of the. controller Y, the operation of the damper 46 being-in general similar to the operation of the valve 68, the damper 46 being brought to such position that the effect of the control current is balanced by the efiect of the difi'erential pressure, and when there is ail-unbalance, the

motor M4 rotates in such direction to move the damper 46 in such direction as to restore a balance. A needle valve 16, or equivalent, may form a bleeder connection between the tubes 12f and 137, as explained in connection with Fig. 5.

' The damper versible motor M5, provided with limit switches and controlled by the control balance Z, whose movable contact 292 connects I with the conductor 66 and whose stationary :municates with the fire box above the fuel bed. As the magnitude of the control current through the fixed and movable coils of.

being adneedle valve or the like.-

d in the breeching, stack orchimney is similarly actuated by the recontroller Z. The pipes 129 and 13g may be connected'by a bleeder pipe, controlledby a needle valve 16 or the like, as explained in connection with Fig. 5. Furthermore, the

ipe 12g, in lieu of connecting with the stack g, may open to atmosphere, as by closing valve 12k and opening valve 126 to atmosphere; and in this latter case the control is effected according to difference between overfire and atmospheric pressure; the bleeder I efi'ectmay be attained by simply bleeding the pipe l3g directly to atmosphere through a The operation of the system indicated in Fi 4 is asfollows:

he pressure of the steam delivered through the pipe 42 from the boiler is permitted to fall temporarily through a suitably small range, asof'the order of twenty pounds per square inch, with increase of load from minimum to maximum, the magnitude of the control current changing inversely with and in definite relation to the change of steam pressure.

' -Accordingly, as the steam pressure falls with increase of load, the. magnitude of the control current increases by a corresponding predetermined amount, with the result that, for a given position of the core A3 of the control coils of the control balance X, the force exerted by the control current upon the balance mechanism increases, throwing the movable system of the balance X out of balance, causing energization of the motor M3, whlch rotates in such d1rect-1on as to actuate the valve 68 in such direction as to further open it and allow delivery ofmore steam to the engine'b, which increases in speed, increasing the rate of delivery of coal or other fuel from the hopper 43 into the fire chamber, the controller Y simultaneously causing energization of the motor M4 to actuate the damper 46 in the air duct 45in such direction as to causev or allow delivery of air to the fuel or fire box at'a correspondingly increasedrate, the effect of increase of supply of fuel and air effecting a greater rate of combustion anda greater rate of steam production. With increased speed of the engine and greater rate of flow of air through the duct 45, the differential pressures exertedvin the controllers X and Y increase until balance is restored and the motors M3 and M4 deenergized.

- The increase in magnitude of the control current through the fixed and movable coils of the controller Z 'unbalances it, causing energization (if the motor M5, which rotates in such direction as to move the damper 615 further toward open position until the increased differential pressure ultimately balances the force exerted by the control coils sure below atmospheric in the furnace above in which case the motor M is deenergized the fuel bed. Such a condition can be defi-,

with the damper d wider open and in a positiom suited tothe increased rate of combustion. t l J In accordance with my invention, as'thus far described, therefor, the magnitude of change of the control current is definitely related to the magnitude of change of steam pressure, the current increasing with decrease of steam pressure, and vice versa. The mechanism which efi'ects a change in magnitude of the control current to accord with change in steam pressure may be considered a master controller which efiects a control of the auxiliary controllers X, Y and Z, as described.

It is generally desirable that the pressure in the header C be maintained substantially constant. The provision of chambers" g1 and d1 connected by tubes el and jl effects, as

.above described in connection with the arrangements of Figs. 1 and 2, restoration of the pressure to a standard value irrespective of the position of contact arms '0 and '1), simultaneously movable by any suitable connection indicated generically by the dash line Z. The adjustment of valve f effects adjustment of the rate of pressure-restoration action.

The rate of deliveryof fuel as controlled by the auxiliary controller X is proportional to the magnitude of the control current, the differential pressure in the controller X being proportional to the square of the speed of the blower'K, and therefore-of the speed ofthe engine 6 and of the stoker mechanism, andthe force exerted by the control current is proportional to the square of the current, whereby the speed of the engine 6 and the rate of delivery of fuel by the stoker is proportional to the control current.

Similarly, as regards the controller Y, the differential pressure exerted thereon is proportional to the square of the rate of flow of airthrough the duct 45, and the electric control force is proportional to the square of the control current, whereby the controller Y functions to maintain a rate of delivery of air twhich is proportional to the control curren When pipe 12g communicates with stack or breeching S and pipe 139 communicates with the furnace, controller Z is responsive to a pressure differential that is substantially proportional to the square of the rate of flow of gases through the heat exchange structure of the boiler and the force exerted by the control current is proportional to the square of that current, whereby the controller Z functions to effect such position of the damper (I that the rate of flow of gases through the heat exchange structure is proportional to the control current.

It is generally desirable to maintain a presnitely secured by leaving pipe 129 open to the atmosphere so that controller Z will operate directly to maintain a furnace suction. The pressure diflerential acting on the balance will then be roportional to the square of the rate of overtlre air supply, whether the latter be by infiltration through the furnace walls or by definitely provided openings. As

the force exerted by the control current is proportional to the square of that current, conbalance the controller when the control current is reduced to zero.

As above described, the master controller establishes, in response to steam pressure variations, predetermined magnitudes of the control current which through the auxiliary controllers efiect rates of delivery of fuel and air, and rates of discharge of gases through the stack S, proportional to the control current, which latter is varied indirect propor- ,tion, but inversely, with changes in steam pressure. Accordingly, upon a decrease of steam pressure, the rate of supply of fuel and air and discharge of gases through the stack S is increased in like proportion to the decrease in steam pressure; and vice versa, with an increase of steam pressure, the auxiliary controllers efi'ect proportionate decreases in rate of delivery of fuel and air and discharge of gases through the stack S.

Furthermore, the ratio between magni-' tude of control current and the rate of flow or delivery of fuel, the rate of flow of air through the duct 45, and the rate of flow of gases to or through the stack S, may be altered or changed in magnitude by adjust ment, as'by discs 26, Fig. 5, to effect adjustment of the cores of the balance coils in any one or more auxiliary controllers, or by effecting an equivalent change in the relation to the actual magnitude of the force pro- 'duced by the electric current to the magnitude of the current; or by the bleeder. action which varies the actual magnitude of the difi'erential pressure exerted upon any or all of the controllers; or both the bleeder action and the matter of adjustment of force exerted by unit. The ammeter I1 indicates the total control current, that is, the sum of the control currents of the boiler unit'branch circuits, and is representative, under stated conditions, of the system demand or load. The setting of the manually adjustable resistance R common to the several control circuits determines the largest value of control current that may flow, and this determines onelimit of control. By short-circuiting the resistances m1 and 4112, control of the boiler system may-be effected by manual variation of resistance R, the operator setting the movable contact to a suitable or desirable point corre' spending with information afiorded by pressure gauges or other devices.

Desired distribution of total s stem load between the several units. may be eflt'ected manually by adjustment of their individual control current limiting resistances 1', the respective ammeters I indicating the value of control current in each control-circuit and under stated conditions, the load carried by the unit. Short-circuitingml, m2, etc. and R,

permits complete manual control of each individual control circuit by variable reslst- The overfire pressure, that is, the pressure inthe region over the fuel bed upon the grate 44, or with which the pipe 13g communicates, is increased either by moving the stack damper (1 toward closed position or by increasing the underfire' air blast pressure. The overfiresuction is .due to the difference between the pressure in the overfire region and atmospheric pressure, and accordingly,

since atmospheric pressure is substantially constant, the overfiresuctlon increases with decrease in overfire pressure.

In accordance with one aspect of my invention, the combustion is controlled so as to increase the overfire suction with change of the steam pressure from a predetermined magnitude. This control is vobtainable by the auxiliary controller Z, as by effecting movement of the stack damper d toward open position in responseto decreasein the steam pressure, thereby reducing the overfire pressure and accordingly increasing the overfire suction. v 7

It is tobe understood'that the term overfire pressure is not restricted to the pressure over a fuel bed or grate but includes the pressure in any furnace chamber, as for example, in a furnace to which liquid, gaseous, or pulverized solid fuel is supplied and in which there is no fuel bed. For brevity in the appended claims, by the term directly? as applied to the response'of 'the auxiliary control to changes in pressure,

orother condition of operation, it is meant that the auxiliary control is not dependent upon a change, for example, in the rate of combustion resulting from the primary control action but responds to the same change which efiects the primary control.

This application is a continuation in part.

of my co-pending application Serial No. 7 56,- 856, filed December 18, 1924.

What I claim is:

1. In the art of controlling the pressure of vapor of a vapor generator, the method which comprises closely following a change in pressure of the vapor by a primary control which substantially immediately changes the rate of vapor generation in accordance with the pressure change, superposing an auxiliary control of the rate of vapor generation directly in response to said change in pressure, and effecting application of said auxiliary control at a rate substantially slower than said primary control.

2. The combination with a vapor-generator, of control mechanism closely following changes in vapor pressure, means controlled by said'mechanism for changing the rate of generation of vapor by said generator substantially immediately to an extent determined by the changes in pressure, and means directly responsive to operation of said control mechanism for superposing an auxiliary control upon said controlled means, to eflt'ect further change in the rate of vapor generation. in the same direction and at a slower rate of change.

3. In a control systemfor vapor generators, control mechanism com rising a controller for changing-the rate 0 va or generation, a movable member, means or moving said member to afiect said controller and closely following changes in magnitude of an operatin condition substantially immediately to c ange the rate of vapor generation to an extent determined by the change of said condition, and means directly re sponslve to movement of said movable mem-' her for applying weight thereto at a rate slower than the rate of movement of said member by'said first means.

4. In acontrol system for vapor-generators, control mechanism comprising a movable member for varying the rate of vapor generation, means closely following changes I in magnitude of an operating condition for moving said member substantially immedi-.

ately to change the rate of vapor generation operating condition substantially immediatei 1y to change the rate of vapor generation to an extent determined hythe change of said condition, of means directly responsive to said changes for applying asupplemental control of the rate of vapor generation at a slower rate.

6. The combination with a vapor generator and means for controlling the rate of vapor generation thereby, said control means closely following changes in vapor demand substantially immediately to change the rate of vapor generation to an extent determined by the change in vapor demand, of means operable upon controlling action of said control means in either sense to effect further change in the rateof vapor generation and at a slow- 4 operating condition, and at a rate substan- .of change.

tially lower than the primary control.

8. In the art of controlling the operation of a vapor generator, the method which con prises efl'eoting change in the rate of vapor generation which closely follows change in an operating, condition and whose extent is dependent upon. said change in said operating condition, and effecting, directly in response to the change in the operating condi-v tion, further change in the rate of vapor generation in the same sense and at a slower rate 9. The combination with a vapor generator, of means for controlling the rate of vapor generation by. said generator, means closely following changes in the vapor pressure for actuating said control means to effect substantially immediate change in the rate of vapor generation to extent determined by the change in pressure, and means directly responsive to operation of control means actuating said control means to effect further change of the rate of vapor generation inthe same direction and at a slower rate of change.

10. A control system comprising means for controlling the rate of vapor generation 1ncluding a movable element, means closely following changes in flow and including movable structure controlling said first means -for changing the rate of vapor generation substantially immediately to extent determined by the change in flow, and means for applying to said movable structure a force, varying with change in position of said movable element but at a slower rate, to efi'ect a supplementary control of the rate of vapor generation.

- 11. "A- control system for a vapor generator vapor generation including responsive means closely following changes in vapor pressure substantially immediately to change the rate of vapor generation to an extent determined 4 by the change in pressure, and means directly responsive to said pressure changes slowly changing the rate of vapor generation to restore said pressure to a predetermined standard within a time interval determined by the extent of said pressure chan e.

EDWARD S. BRI TOL.

comprising means for controlling the rate of 

